Speed control linkage means for winding bobbins

ABSTRACT

A bobbin winding means in textile machinery having a driven spindle for the bobbin and a roller means in contact with the peripheral surface of the bobbin in a closed drive position thereof, the drive means for said bobbin including a friction gear for variation of the speed of revolution of the bobbin in response to increasing diameter of the bobbin by means of a speed control linkage means adapted to actuate a lever adjusting means on the friction gear in response to relative displacement between the bobbin spindle and the roller means, this linkage means having yielding elements which move as a single-acting unit during normal drive of the bobbin but which can be pressured or adjusted into an open position freeing the bobbin from contact with the roller means when the bobbin drive is stopped.

United States Patent [1 1 I Grein et al.

[ SPEED CONTROL LINKAGE MEANS FOR WINDING BOBBINS [75] Inventors:Hermann Grein, Remscheid; Volker Vorlander, Berlin, both of GermanyBarmag Barmer Maschinenfabrik Aktiengesellschaft, Wuppertal, Germany 22Filed: July2, 1971 211 Appl. No.: 159,418

[73] Assignee:

[30] Foreign Application Priority Data Germany P 20 33 578.8

July 7, 1973 [52] US. Cl 242/18 CS, 242/45; 242/67.5 g [51] Int. Cl B65h59/38 [58] Field of Search 242/18 CS, .18 R, 242/45, 67.5, 75.5;74/190,1905, -l9l, 194, 198, 199

[56] References Cited UNITED STATES PATENTS 2,093,820 9/l937Siegenthaler 242/18 CS. 2.568.960 9/1951 Kershaw 242/18 CS vFOREIGNPATENTS OR APPLICATIONS 525,711 5/l93l Germany 242/18 CS Dec. 18, 1973418,531 10/1934 Great Britain; 242/18 CS 1,156.625 7/1969 Great Britain242/18 cs 208,123 4/1940 Switzerland 242/18 cs Primary Examiner- StanleyN. Gilreath Attorney-Johnston, Root, OKeeffe, Keil, Thompson & Shurtleff[5 7] ABSTRACT A bobbin winding means in textile machinery having adriven spindle for the bobbin and a roller means in contact with theperipheral surface of the bobbin in a closed drive position thereof, thedrive means for said bobbin including a friction gear for variation ofthe speed of revolution of the bobbin in response to increasing diameterof the bobbin by means of a speed 1 control linkage means adapted toactuate a lever adjusting means on the friction gear in response torelative displacement between the bobbin spindle and the roller means,this linkage means having yielding elements which move as asingle-acting unit during normal drive of the bobbin but which can bepressured or adjusted into an open position freeing the bobbin fromcontact with the roller means when the bobbin'drive is stopped.

12 Claims, 8 Drawing Figures PMFNTEDUEU 8 1915 3,779,471

sum 1n; 3

FIGI

1 NVZLVIORS HERMANN GREIN VOLKER VORLANDER ATT'YS PATENTEn'uzc 1 8 ms 3;779.471 sum 3 OF 3 HERMANN GREIN VOLKER VVORLANDER ATT'YS 1 SPEEDCONTROL LINKAGE MEANS 'FOR WINDING ROBBINS This invention generallyrelates to textile machinery such as spinning, spooling or twistingmachines equipped with a speed variation gear means in .the drive of athread or yarn winding position, such gear means being adjustable over alinkage or lever system connected to elements of the winding positionwhich move out or swing out in response to the increase of the windingdiameter, e.g., the growing diameter of a wound bobbin. I I

In the'winding of threads, yarns and the like which are supplied to thebobbin of a winding position at a constant rate of speed, the depositingspeed of the thread on the winding surface of the bobbin must alsoremain constant during the entire'win'cling process. in order to achievethis, as is well known, the turning speed of the bobbin being wound iscaused to decrease as the winding diameter increases.

ln orderto control this'bobbin rate of revolution, it is thus aknow npractice todrive the bobbin on its winding circumference by means of adrive roller frictionally engaging'the bobbin and turning at a constantrate, whereby the. bobbin turning rate is continuously automaticallyadjusted in correspondence to the constant peripheral velocity appliedthereto. For a number of practical reasons, this type of peripheraldrive of the bobbin is not desirable, especially where the wound threadsmay be easily damaged.

in the case of a winding bobbin driven only at its spindle or axis,however, this constantspeed control of the peripheral surface of thebobbin is I not possible. In these cases, the shifting movement of thebobbin axis or, in the case of a bobbin arranged in fixed position, of afeeler roller lying against the winding surface, is employed in order toadjust the bobbin drive motor directly over a lever rod system-or othersuitable linkage means. When interposing a speed varying gear means,this linkage means can be used to adjust the gear in the sense ofcausing-a speed reduction as the bobbindiamcter increases.

vicing of the machine. Another object of the invention consists inmaking possible the described pivoting or displacing movement of theparticular element of the winding position which is gradually shifted bythe increasing bobbin diameter, not only during winding but also withthe gear at a standstill and without dismantling or removing theadjusting linkage means.

These and other objects and advantages of the invention will become moreapparent upon consideration of the following detailed specification.

It has now been found, in accordance with the invention, that thedesired access and servicingof the winding position in the textilemachine can be achieved in those instances whereinthe winding means of atextile machine includes spindle means for rotational winding of athread onto a bottin and roller means arranged to I contact the outerperipheral surface of the bobbin dur- These gear means are generallyconstructed as infinitely variable frictiongears, this being-arelatively simling the speed of the winding bobbins. With themachine ata standstill, however, such a friction gear because of its extremefriction cannot be directlyv adjusted. As a consequence of this freezingor fixation of the gear, the pivotal movement or displacement'of thebobbin spindle (or else'the feeler roller) with reference to itscounterpart which is on a fixed axis at the winding position is notpossible, for example, for the purpose of changing a bobbin or retying abroken thread. The usual locked gear-adjusting linkage means under thesecircumstances thus prevents easy removal or access to the bobbin. Thispivotal movement or displacement is possible as between the bobbinspindle and a contacting roller only if previously the friction gear hasbeen mechanically disassembled from the adjusting linkage or else theadjusting linkage itself has been separated mechanically fromthedisplaced or pivoted element of the winding position. Such aservicing of the machine is, however, overly complicated andtime-consuming.

Oneobject of the present invention to remedy the disadvantages of theknown winding devices in textile machines and to make possible an easyand rapid sering winding thereof, these spindle and roller means beingmounted for displacement relative to each other in response toincreasing bobbin diameter, and drive means for rotation of the bobbinon the spindle means by operation through an infinitely variablefriction gear having a speed adjusting leverthereon which is movableonly during the driven rotation of the gear, by providingthe improvementwhich comprises a speed control linkage means connected to the speedadjusting lever for movement thereof in response to variations in thedisplacement between the spindle and-roller means, this linkage meansincluding yielding coupling means or connecting elements operating as asingle-acting linkage unit during the driven rotation of the bobbin butyielding under an applied pressure which moves the bobbin away from itscontacting roller means while the sist essentially of a slip coupling ora so-called slipper or release clutch, whose slipping, shifting orrotary movement either along a rod or the like or else about an axis orpivot point is preferably limited in one or both directions by a stopmember which may be adjustable. In the lifting off or displacement ofthe winding bobbin or of the feeler roller, its carrier arm is movedorswung into any desired override position, in which operation the slipcoupling yields correspondingly. The resetting of the carrier arm mustthen take place up to the stop member of the slip coupling, so that thewinding bobbin or feeler roller carrier arm passes back into itsoriginal starting position, i.e., at any point in the overall windingoperation.

A further desirable feature of the invention is one in which thestarting position is automatically reoccupied after the deflection orshifting of the carrier arm to its override position in order to servicethe bobbin. This is accomplished, in accordance with the invention byproviding as the yielding coupling means in the gear adjusting linkagemeans,,a fulcrumed or two-armed coupling pivoting on a fixed pivotpoint, in which both lever arms are arranged to pivot with respect toone another and are preferably braced or tensioned against one anotherby means of an adjustable stop and spring means. The bobbin carrying armor the carrying arm of the feeler roller can in this manner be manuallydeflected or urged from its normal contact or engaging position of thebobbin and roller means by overriding the spring tensioning force, sothat an easy bobbin change or knotting operation is possible. Thecarrier arm, after removing the deflecting force, then returns back intoits starting position under the influence of the spring force. The pivotaxis or pin connecting the two lever arm of the spring-urged leversystem with one another can simultaneously act as the fixed pivot axisor pin of the lever system as such, i.e.,'as the pivot means forrelativemovement of both coupling lever arms and also for the coupling member asa single-acting linkage unit. It is, however, equally suitable toconstruct the two axes or pins separately and to articulate or pivot oneof the two lever arms on the other. 7

The connection between the yielding coupling of the linkage means withthe adjustable member of the friction gear can also be established overa separate coupling rod. In this case, the slip coupling is thenpreferably arranged on the coupling rod or else the selfyielding(spring-tensioned) lever system is articulated or pivoted on the'separate coupling rod.

The slip coupling or yielding connecting elements of the gear-adjustinglinkage means can also be located at the pivot point or axis of thecarrying arm for the bobbin spindle or the feeler roller, so that thiscarrying arm is yieldingly connected with a rocking lever which engagesat its other end into'the guide slot of a cammed rocker arm or platewhich also has a predetermined cam surface or rail portion adapted to,guide the adjusting member of the friction gear. With the preferred useof the resilient or spring-tensioned two arm lever connection pivotedabout a' fixed pivot point, one of the two lever arms can be equippedwith a cammed rocker arm which guides the adjusting member of thefriction gear.

The cammed rocker arm' can be constructed as a contoured single-rail camsurface and also as a two-rail slot. In the case of single-railconstruction of the cam, the yielding deflection or lateral movement ofthe bob-' bin or feeler roller carrying arm takes place in opposition orin contrast to the fixed position of the rocker arm brought to astandstill by the blocked or frozen gear-adjusting member. There is thenno check rail or bar in the way of a return of the bobbin or feelerroller carrying arm. It is possible, therefore, without difficulty toautomatically return the individual elements up to the contact of thebobbin and feeler roller at their original position before deflection ordisplacement from each other. The restoration of the gear adjustingmember into its original position must be accomplished in this instanceby a spring or similar elastic means, so that the gear adjusting memberenters intoor remains in contact with the guide rail of the cammedrocker arm as soon as the machine is switched on again.

In the case of the two-rail or slotted construction of the cammed rockerarm, the adjusting lever member of the friction gear is always guided onboth sides and can therefore be adjusted only by the movement of therocking lever and permits, on its part, a shifting of the cammed rockerarm only when the gear is turning. Consequently, after removing a fullor partly wound bobbin and inserting a new spool or tube on a machine ata standstill, there does not immediately arise any contact between thefresh bobbin spool and the feeler roller. As soon as the machine beginsto run, however, the counterweight of the bobbin carrying arm or else apull spring or the like on the adjusting lever member of the frictiongear is utilized to urge the bobbin carrier arm into the fresh windingposition. This same pull spring acts oppositely to the release oroverride direction of the deflected carrier arm so that it can also actto draw the carrier arm back to any intermediate position of windingwhen used in cooperation with a suitable stop member.

The guide rail or slot of the cammed rocker arm in running contact withthe gear adjusting lever can be constructed over its entire length insuch a way that from the start of winding onward there is provided apredetermined reduction of the bobbin turning rate, i.e., its speed ofrevolution. However, in order to facilitate the start of the winding ofthe thread on the bobbin, for example in order to reach a desiredwinding speed or draw-off speed from the feed bobbin or to generate firmthread lays on the winding spool as a stable basis for the building upof the rest of the wound bobbin, it is also expedient in some instancesto avoid changing the winding speed up to a certain spool diameter, tochange it only very slightly and then only later to begin the gradualcontrolling down of the bobbin turning rate. This is achieved accordingto the invention by providing the guide rail or slot of the cammedrocker arm designed to receive the gear adjusting member with an initialguide zone corresponding to the winding commencement such that the guiderail has at this point a radius of curvature identical with the turningradius of the cammed rocker arm measured from its pivot point, or elsethis guide rail lies tangentially or secantially to this swinging are orcircular segment. In traveling through this initial guide zone, a smallportion of the resulting winding can be formed with a winding speedwhich increases in dependence on the growth of the winding diameter.Thus, the invention also permits to at least some degree a variableprogramming of the winding speed by the cam arrangement.

These and similar equivalent embodiments of the invention areillustrated in greater detail by the examples given in the accompanyingdrawing wherein: 7 FIG. 1 is a partly schematic side elevational view ofa winding unit in which the speed control linkage means has a linearslip coupling assembly between a pivoted carrier arm for the bobbin andan adjusting lever on the friction gear of the drive means;

FIG. 2 is a partly schematic side elevational view of a similar windingunit in which a rotational slip coupling assembly is provided in thespeed control linkage me FIG. 3 is a partly schematic side elevationalview of still another embodiment of the winding unit in which theyielding coupling means for the speed control linkage is provided by twolevers braced against each other in a toggle lever arrangement;

FIG. 3a is an enlarged partial perspective view of the toggle leverprovided with an adjustable stop means along one lever arm thereof;

FIG. 4 is a modified embodiment of the winding unit shown in FIG. 3wherein one of the tensioned coupling lever arms of the toggle leverarrangement is equipped with a cammed plate to provide a guide slot forthe gear speed adjusting lever;

FIG. 4a is an enlarged partial perspective view of the toggle lever andstop member used in the embodiment of FIG. 4;

FIG. 5 is a partial side elevational view of the bobbin and its carrierarm pivoted away from a supporting roller for exchanging or servicingthe bobbin, two suitable blocking or temporary holding means for thisopen position being illustrated; and

FIG. 6 is a fragmentary side view of a cammed rocker arm or guide railmember, illustrating the manner in which the speed control can bemechanically programmed.

Similar parts in each of the various embodiments have been designated bysimilar reference numerals even though there may be slight variations inthe design or placement'of such parts. I

Referring generally to FIGs. 1 to 4, there is represented a singlewinding position of a typical textile spinning, spooling or twistingmachine, i.e., there usually being a very. large number of winding unitsarranged side by side along a supporting frame. The winding drive takesplace in all cases from the motor 1 or a chain, belt or cord 2 leadingfrom any drive shaft onto the infinitely variable friction gear 3 andthen further in a conventional manner over belt 4, deflection rollers 5and belt 6 onto the bobbin holder or spindle 7, the wound package .8 ofthread or yarn being taken up on the bobbin tube 9 which can be slippedover the holder or spindle'7.

The bobbin holder 7 is supported by a carrying arm borne to pivot on thefixed pivot pin 11, and this arm 10 is weighted in such a way that theempty bobbin tube 9 or the resulting winding or bobbin 8 always tends tolean against the supporting roller 12 having'its axis of rotation in afixed position. The thread or yarn l3-runs from a thread guide and anysuitable feed roll or other supply means (not illustrated) onto thisroller 12 before it is deposited on the winding surface of the tube 9 orbobbin 8. Between the carrying arm 10 and the adjustable member or speedcontrol settinglever 14 of the gear 3, there is arranged the linkagemeans as a gear shifting system equipped according to the invention witha yielding coupling means or connecting elements in a pretensioned orfrictionally engaged closed operating position. Different yieldingcouplers or slip clutch arrangements are illustrated in the drawings,and still other variations are obviously also suitable.

According to FIG. 1, the coupling means consists of the rocking lever 15rigidly fastened to the carrying arm 10 in combination with the couplingrod 16 pivotally connected on the adjusting lever 14 and provided withstop 17 at the opposite end. A slip coupling is accomplished in thesimplest case by means of sleevel8 and spring 19 as means sliding on therod 16 against a certain predetermined resistance, this sleeve 18 beingjoined at 20 with the other end of the rocking lever 15. A pull spring21 engaging on the control or adjusting lever 14 loads or urges thiscontrol leverof the friction gear 3 in the sense of causing a clockwisemovement for speed increase. Also, when the gear 3 is engaged during thedrive of the winding unit, this spring 21 with the stop member 17 alwayensures that a contact engagementof the bobbin winding 8 or of the tube9 on the supporting roller 12 is achieved and the speed control ismaintained. The clamping effect of the slip coupling elements l6, l8 and19, i.e., as exerted by the spring clamp in sleeve 18, is chosen so asto be greater than the pull or displacing influence of the spring 21 onthe coupling rod 16. During the winding, this prevents the occurrence ofa false speed or turning rate by inadvertent coupling slippage.

For the changing of bobbins or for tying of a broken thread, it is nowpossible with the apparatus illustrated in FIG. 1, despite the immovableor fixed adjusting lever 14 with the motor at a standstill, for thebobbin carrying arm 10 to be pivoted off from the supporting roller 12through the yielding or override movement of the slip coupling.Moreover, this easily manipulated pivotal release of the bobbin from itsassociated roller does not require a mechanical separation ordisassembly of the speed control linkage or the gear portion of thedrive means. After completion of the bobbin change or knottingoperation, the swinging arm 10 is pushed back or falls back under itsown weight until the sleeve 18 of the slip coupling again touches thestop member '17. A freshly slipped on empty bobbin tube or spool 9 doesnot at first apply itself to the supporting roller 12, since the blockedor frozen adjusting lever 14 prevents any further swinging back of thecarrying arm 10. With starting of the motor I and the belt drive 2,however, this blocking of the gear control or adjusting lever 14 isdiscontinued, so that the carrying arm can then turn under the influenceof its weight and/or the pull of spring 14 clockwise up to engagement ofthe fresh tube 9 against the supporting roller 12.

FIG. 2 illustrates, in place of the slip coupling of FIG. 1, a twist orrotational slip coupling 22, which acts on the fixed axis 11 between thecarrying arm 10 and the rocking lever 15'. This rotational or torsionalslip coupling is formed in a conventional manner by axial elasticbracing of annular friction surfaces, i.e., where oppositely disposedannular members are frictionally engaged about the pivot axis 1 l. Theconstruction of such rotational slip couplings as such is well known andtherefore does not require a separate detailed description.

The rocking lever'l5' engages at its other end into a groove orslot-type guide track 23 of a cam lever 25 which rocks or pivots aroundthe fixed position of the pivot pin at 24. The guide slot 26 of this camlever 25 shifts the lever 14 of the friction gear 3 against the actionof the pull spring 21' during increase of the winding diameter whichresults in a reduction of the bobbin or spindle turning rate. The mannerin which this device functions corresponds substantially to thatdescribed for FIG. 1 except that the direction of speed control of thelever 14is reversed. Again, after completion of a bobbin change orthread retying operation, the carrying arm 10 must be turned back untilit lies against the stop 27 located on the arm 10 and limiting themovement of the rocking lever 15'.

In FIGS. 3 and 4 the yielding coupling means is 7 formed, in contrast tothe slip couplings of FIGS. 1 and 2, is formed as a flexibletogglelever, i.e. a two-armed lever which is resiliently moved into an openposition increasing the angle between the arms. Also in FIGS. 3 and 4 asin FIG. 1, the rocking leverlS is fastened rigidly to the pivoted bobbincarrying arm 10 turning or pivoting about the fixed axis 1 1. On a fixedaxis or pivot 28, there are pivotally or turnably connected the levers29 and 30. A tensioned pull spring 31 connected at either end to thesetwo levers '29 and 30 urges the lever 29 constantly against thestop 32seated on the upper edge of lever 30 (see especially FIGS. 3a and 4a).

Lever 29 has at its other end a slot or groove 33, into which therocking lever is slidingly engaged. Lever 30 is then connected at itsother end, according to FIG. 3, over the coupling rod 16 or, accordingto FIG. 4, over the cammed rocker arm 34 onto the adjusting lever 14 ofthe friction gear 3.

The pull spring 21 or 21' engages as shown in both FIGS. 3 and 4 on theadjusting lever 14 in the sense of directing a faster turning rate and aswinging of the carrying arm' 10 toward the supporting roller 12 whenthe winding drive is in operation. Spring 31 or 31 is sufficientlystrongly tensioned that the levers 29 and 30 or 30' cannot leave theirnormal stop position resulting from the stop member 32 or 32 under theforces conducted from spring2l or 21' into the linking rod assembly.Thus, it is essential for the pulling force of spring 31 or 31' to besubstantially greater than the spring force of the corresponding controllever spring 21 or 21 At the same time, these are not exceptionallylarge spring forces so that one can manually override the pull forceexerted by spring 31 or 31' in order to retract or swing out the carrierarm 11 and its spool 9 or bobbin 8 on the spindle means 7. Absent thisoverriding movement, on the other hand, the spring 31 or 31 doescooperate with stop member 32 or 32' to provide a single-acting two-armlinkage unit.

Through this type of yielding connection or resilient coupling there isalways assured for'the entire course of the winding process asubstantially faultless guiding of the speed control lever 14, while ata standstill or non-driven condition of the friction gear 3, the bobbincarrying arm 10 can still be moved against the pull of the spring 31 or31' away from the supporting roller 12 without being hampered ordisturbed by the blocked control lever 14.

The stop member of the yielding coupling means or connecting elements inthe linkage assembly is preferably constructed and arranged in anadjustable manner as indicated in the embodiments of FIGS. 1, 3 and 3a.For example, as shown in FIG. 1, the knurled stop nut 17 can beadjustably threaded on the linking rod 16 so as to place it at differentpositions from the free end of this linking rod opposite its connectionto control lever 14. This naturally permits a considerable variation inthe initial setting of the speed control means including lever 14. Asshown in the two-arm lever arrangement of the coupling means in FIGS. 3and 3a, the stop member 32 is adapted to slide along the upper edge ofthe lever arm 30 behind the pivot pin 28, and this stop 32 can beremovably tightened at any position thereon by means of the lock screw36 or any similar locking or clamping means.

As indicated in FIG.'4a, the stop member 32' can also be in a fixedposition on the lever arm 30, but in this instance, other means foradjusting the initial speed control setting of the friction gear 3should preferably be provided. For example, as indicated in FIG. 4, theslotted cam plate 34 can be attached by a pair of slot and bolt means 37which permit an adjustment of the guide slot 26 to different initialsettings of control lever 14. This also permits an easy interchange ofdifferent cam plates 34 so as to provide some differences in thedimensions and resulting winding program established by the guide slot26. V

In FIG. 5, the bobbin 8 with the spindle and spool elements 7 and 9carried by arm 10 are illustrated after i being swung about pivot 11 upto an almost vertical position at a substantial distance away fromroller 12 so as to replace the bobbin or tie the broken thread 13. Inorder to carry out such operations without manually holding the windingmeans and carrier 10 in this open position, it is preferable to insert aretractable blocking member 38 of any suitable design and arrangementand/or to provide a handle member 39 which serves to pull'the bobbin 8and arm 10 away from roller 12, e.g., by a pin 40 insertable in acorresponding hole or depression in the carrying arm 10. Individualholding or catch members 41, which may also be an elongated bar or railalong the machine or part of a portable workbench or the like, can bepositioned to lock the handle member 39 in place until it is lifted orremoved to release the bobbin back into its normal winding position.Other temporary locking or holding means are also quite suitable,provided that once they are released, the spring 31 or 31 will pull thebobbin carrying arm 10 back into its original starting or intermediatewinding position.

In the construction of the pivoted axis or bearing pin of the two levers29 and 30, one can also readily visualize a construction in which onlythe lever 30 is borne on the fixed axis or pin 28 while lever 29 ispivoted or hinged on the lever 30. A reversal of this arrangement,namely lever 29 pivoted on axis 28 and lever 30 pivoted on lever 29 isat least feasiblein the case of a device equipped with the coupling rod16' according to. FIG.

FIG. 6 shows, in a fragmentary view, the course of curvature of a cammedrocker arm 34' along its guide edge or rail 35. This rail at itsindicated end 35 is first directed uniformly at the winding commencementso as to exhibit a radius of curvature R which is about identical to theswinging radius of this initial zone of the guide edge about the fixedaxis or pivot point P (corresponding to axis 24 in FIG. 2 or axis 28 inFIG. 4). At the start of the winding process then, in spite of the firstslight increase of the bobbin diameter and corresponding displacement ofthe cammed rocker arm 34', there does not immediately occur any changeof the turning rate of the bobbin or its spindle, so that the thread inthis initial winding stage is wound with a slightly increasing volocityof the bobbin. When the desired winding speed is subsequently attainedor the requisite base thread layers have been properly distributed onthe tube at the end of this first winding stage, the lever 14 then movesout of the influence free guide range 35 of radius R on the rocker arm34' into its active control or deflecting zone 35 which then bringsabout the desired reduction of the bobbin turning rate .with increasingbobbin diameter.

During normal operation of the winding means, the speed control linkageassembly of the invention can operate as a single-acting programmed unitwhich is entirely responsive to changes in the bobbin diameter. When thewinding operation is stopped for servicing, however, the yieldingcoupling means or coacting resilient elements of this linkage assemblypermit a rapid manual disengagement of the bobbin from its associatedcontact roller, and after the pressure exerted to cause thisdisengagement has been released, the bobbin can be automaticallyreturned to its last normal operating position without restartingthe'winding. Moreover, even when replacing a fully wound bobbin with anyempty spool or tube, this freshly loaded spindle of the 1. incombination with the winding means of a textile machine includingspindle means for rotational winding of a thread onto a bobbin androller means arranged to contact the outer peripheral surface of thebobbin during winding thereof, said spindle and roller means beingmounted for displacement relative to each other in response toincreasing bobbin diameter, and'drive means for rotation of said bobbinon said spindle means by operation .through an infinitely variablefriction gear having a speed adjusting lever thereon which is movableonly during the driven rotation of the gear, the improvement comprisinga speed control linkage means connected to said speed adjusting leverfor movement thereof in response to variations in the displacementbetween said spindle and roller means, said linkage means includingyielding coupling means operating as a single-acting linkage unit duringthe driven rotation of the bobbin but yielding under an applied pressuremoving said bobbin and said contacting roller means away from each otherwhile said drive means is stopped with said adjustable lever in a fixedposition.

2. The combination as claimed in claim 1 wherein said yielding couplingmeans is formed by a slip coupling of two surfaces in frictionalengagement with each other and limited in the amount of slip by a stopmember.

3. The combination as claimed in claim 2 wherein said stop member isadjustable to provide a predetermined variation in the dimensions andposition of the slip coupling members in the linkage means.

4. The combination as claimed in claim 1 wherein said yielding couplingmeans includes a pair of lever arms pivoted with respect to each otherand spring tensioned to pivot apart until restrained by a stop memberconnected to one of the lever arms.

5. The combination as claimed in claim 4 wherein said stop member isadjustably connected to said one of the lever arms.

6. The combination as claimed'in claim 4 wherein said yielding couplingmeans as a single acting linkage unit is essentially in the form of arocker mounted to pivot on a fixed axis which simultaneously providesthe pivot axis of said pair of spring tensioned lever arms.

7. The combination as claimed in claim 2 wherein the slip coupling isarranged on a connecting rod which in turn is pivoted on a speedadjusting control lever of the friction gear.

8. The combination as claimed in claim 4 wherein the pivoted and springtensioned lever arms of the yielding coupling means are pivotallyconnected near one end of a connecting rod which has its opposite endpivotally connected onto a speed adjusting control lever of the frictiongear.

. 9. The combination as claimed in claim 2 wherein the slip coupling isarranged at the pivot point of the carrying arm of the bobbin or itsassociated roller means, said slip coupling connecting said carrying armwith a rocking lever which is engaged at its other end into guide meansof a cammed rocker arm pivoted on a fixed axis and provided with acammed surface adapted to guide the speed adjusting control lever of thefriction gear.

10. The combination as claimed in claim 4 wherein one of the two leverarms pivoted on a fixed axis is attached to a cammed rocker arm having aguide means adapted to guide an adjustable speed control lever of thefriction gear.

11. The combination as claimed in claim 9 wherein the initial startingzone of the cammed rocker arm guide means has a radius of curvatureapproximately equal to the swinging radius of the rocker arm measuredfrom its fixed pivot point.

sured from its fixed pivot point.

UNITED STATES PATENT OFFICE OERTEFMATE ORRECTION Patent No. Q7'ITQ LI"Z1 Dated l hgr J! 121.3

l fl Hermann Grein and Volkerc Vorlander It is certified that errorappears in the above-identified patent and that said Letters Patent arehereby corrected as shown below:

First page, left-hand column, eleventh line, Priority Date "July 7,1973" should read July 7, 1970 Column 3, line 11, "arm" should read armsSigned and sealed this 22nd day of October 1974.

(SEAL) Attest:

MCCOY M. GIBSON JR. Attesting Officer C. MARSHALL DANN Commissioner ofPatents FORM PO-1050 (10-69) I uscoMM-oc 60376-P69 fir U.S. GOVERNME NTPRINTING OFFICE: i969 0-366-334,

1. In combination with the winding means of a textile machine includingspindle means for rotational winding of a thread onto a bobbin androller means arranged to contact the outer peripheral surface of thebobbin during winding thereof, said spindle and roller means beingmounted for displacement relative to each other in response toincreasing bobbin diameter, and drive means for rotation of said bobbinon said spindle means by operation through an infinitely variablefriction gear having a speed adjusting lever thereon which is movableonly during the driven rotation of the gear, the improvement comprisinga speed control linkage means connected to said speed adjusting leverfor movement thereof in response to variations in the displacementbetween said spindle and roller means, said linkage means includingyielding coupling means operating as a single-acting linkage unit duringthe driven rotation of the bobbin but yielding under an applied pressuremoving said bobbin and said contacting roller means away from each otherwhile said drive means is stopped with said adjustable lever in a fixedposition.
 2. The combination as claimed in claim 1 wherein said yieldingcoupling means is formed by a slip coupling of two surfaces infrictional engagement with each other and limited in the amount of slipby a stop member.
 3. The combination as claimed in claim 2 wherein saidstop member is adjustable to provide a predetermined variation in thedimensions and position of the slip coupling members in the linkagemeans.
 4. The combination as claimed in claim 1 wherein said yieldingcoupling means includes a pair of lever arms pivoted with respect toeach other and spring tensioned to pivot apart until restrained by astop member connected to one of the lever arms.
 5. The combination asclaimed in claim 4 wherein said stop member is adjustably connected tosaid one of the lever arms.
 6. The combination as claimed in claim 4wherein said yielding coupling means as a single acting linkage unit isessentially in the form of a rocker mounted to pivot on a fixed axiswhich simultaneously provides the pivot axis of said pair of springtensioned lever arms.
 7. The combination as claimed in claim 2 whereinthe slip coupling is arranged on a connecting rod which in turn ispivoted on a speed adjusting control lever of the friction gear.
 8. Thecombination as claimed in claim 4 wherein the pivoted and springtensioned lever arms of the yielding coupling means are pivotallyconnected near one end of a connecting rod which has its opposite endpivotally connected onto a speed adjusting control lever of the frictiongear.
 9. The combination as claimed in claim 2 wherein the slip couplingis arranged at the pivot point of the carrying arm of the bobbin or itsassociated roller means, said slip coupling connecting said carrying armwith a rocking lever which is engaged at its other end into guide meansof a cammed rocker arm pivoted on a fixed axis and provided with acammed surface adapted to guide the speed adjusting control lever of thefriction gear.
 10. The combination as claimed in claim 4 wherein one ofthe two lever arms pivoted on a fixed axis is attached to a cammedrocker arm having a guide means adapted to guide an adjustable speedcontrol lever of the friction gear.
 11. The combination as claimed inclaim 9 wherein the initial starting zone of the cammed rocker arm guidemeans has a radius of curvature approximately equal to the swingingradius of the rocker arm measured from its fixed pivot point.
 12. Thecombination as claimed in claim 10 wherein the initial starting zone ofthe cammed rocker arm guide means has a radius of curvatureapproximately equal to the swinging radius of the rocker arm measuredfrom its fixed pivot point.